Rotary turbine pump



Dec. 9, 1952 G, F, BAEZ 2,620,735A

-ROTARY TURBINE PUMP Dec. 9, 1952 G, F, BAEZ 2,620,735

ROTARY TURBINE PUMP Filed Jan. 18, 1951 2 'SHEETS-SHEET 2 l ,f/\ f2 9 22 1|," f/ 21 m 4 Mw wl l Patented Dee. 9, r1952 UNIT ED S TATE S SPATEN T OFF l C E ROTARY TURBINE lPUMP Guillermo lFederico Baez, Buenos Aires, Argentina Application January 18, 1'951, VSerial No. 206,545

1 The present invention relates to pumps Aand more particularly to rotary turbine pumps and has for its object to provide an improved rotary turbine pump which, while of comparatively simple construction, offers va number of advantages over known pump constructions.

Another object of the invention is to provide a pumping apparatus A-having a greater lifting power than a centrifugal pumpof similar dimensions.

A further object of the invention is to provide a pump having a greater capacity than the conventional gear pumps of similar dimensions.

With these and various other objects -in view the invention consists of certain novel 'features of construction and operation and will be more fully described and particularly pointed out in the fol-- lowing description and drawings.

In the drawings, wherein like reference characters are vused to designate likeparts,

Fig. 1 is a longitudinal section of the rotary turbine pump according to the invention.

Fig. 2 is a fragmentary perspective view of the novel pump, and

Fig. 3 isa part sectional end view looking axially towards the inlet end.

Referring now to Figures l and 2, the pump comprises a casing il, the maximum diameter of which is such that it may be lowered into a well casing'2. 'Casing 'I is formed at the 'lower end thereof with a constricted inlet 3, which may be externally screw threaded asindicated at 4, and provided with a polygonal nutlike portion 5 vtoen- `able an accessory such as a lter unit to be conveniently screw connected thereto. IThe end of the .casing remote from the .inlet 3, is internally -screw threaded asat 6 to receive an externally threaded spigot I of a head member 8. Said head member 8 has projecting from the end thereof remote from the spigot 1 a dischargeextension indicated by the ,general reference 9, the free end of which is externally threaded as at I0 for connection to a delivery pipe not shown. The outlet extension is hollow to provide a passage I'I which in the neighbourhood of the free lend of said extension is substantially circular in cross section-and of diameter substantially equal to the bore of such delivery pipe. From said free end towards the head memb'er, said passage becomes constricted in one direction and gradually widened in an arcuate direction so as to have a gradually increasing, roughly kidney shape section and to meet over a considerable arc of a circle an annular, lengthwise arcuate chamber I2, formed in the end of said spigot and extending inwardly thereof in a generally axial direction. Fixedly secured inside chamber I2 is a set of Z Glaims. (Cl. 10S-9d) radial, lcircumferentially spaced `and axially inclined stator blades I3 arranged lata certain distance from the top of said chamber so as to leave an annular space Y'Iii therebetween. I-lead member 8 including spigot i has a centrally disposed,

substantially axial, stepped bore, indicated generally by reference character I5, which bore extends through said head member on the inside of the annular chamber I2, from which it is separated by an annular wall portion I-G. Starting from the free end-of the spigot 'I, said stepped bore I5 comprises a relatively wide cylindrical portion il', extending axially towards the body of lthe head member where said relatively wide portion?! l vmeets a cylindrical portion I 8 of small- -er diameter and coaxial with said relatively wide portion thereby forming an internal annular step I9. The narrower bore portion I8 at its -end remote from the wider portion meets a frustoconical bore portion 2i) whereby it is connected 'to a still narrower relatively short cylindrical bore portion 2|, `between which and the end of the head member 8 remote from the spigot 'I one or more stepped portions are formed as at 22 of a diameter adapted to receive a suitable thrust bearing, for instance, a ball thrust bearing 23. In the relatively wide bore portion I'I, a packing member 2li is housed, which packing member `is adapted to be compressed axially as by an annular externally threaded pressure ring 25, screwed into the mouth of said relatively wide vbore portion II, which mouth is to this end screw threaded as indicated at 26. Packing member 2li is cylindrical and its bore of substantially the same diameter as the narrow cylindrical bore portion I3.

It will be observed that any compression exerted axially of the packing member 2, by the screw ring 25, is taken up by said annular `step vor shoulder I9 and that with the packing member 2.4 and the screw ring 25 inserted into the relatively wide bore portion I'I there is dened within the head member 8 a substantially cylindrical coaxial space which extends from the free end of :the spigot l axially of the head member to meet the frusto-conical portion '253 of the stepped bore I5, said space being adapted to receive a shank 2l ofa main rotor 28 including .a head 29 having a pluralitypof rotor blades 3i) extending outwardly from its circumference, said .head being secured to said shank Yas by grub screws 29a. Said shank extends from one side of said head 28 and is substantially cylindrical over an axial distance sufficiently longer than the depth of the aforesaid cylindrical space to provide for suiiicient clearance between the end face 3l of said spigot and the rear annular face 32 of said head 2S formed between the periphery of the head and an annular recess 29h provided in the end of said head adjacent the spigot. Beyond the cylindrical portion aforesaid the shank 2? is reduced in diameter by means of a frusto-conical reduction 33 adapted to engage the frusto-conical bore portion 20 and to provide a cylindrical bearing portion 34, the extreme end cf which is adapted to have mounted thereon and secured thereto as by grub screws 35a, a bevel gear 35. The arrangement is such that the annular face 36 formed between the toothed portion 3l of said bevel gear 35 and that the neck 38 thereof will normally seat on the thrust bearing 23. The shank 2l of main rotor member 28 is centrally and axially bored as at 39 to receive a driving shaft 4Q.

Conveniently, a portion or" said bore 39 extending from the free end of the shank 2l inwardly for a suitable distance is enlarged to provide a packing chamber lli adapted to receive a cylindrical packing member #i2 which, like the packing member gli may be retained in the packing chamber by a retaining ring d3 screwed into the mouth of said packing chamber 4i. Said driving shaft iii is adapted to project beyond the outer surface i4 of the retaining ring 43 and has secured thereto as by grub screws lila a secondary rotor member 45 generally similar to the head E9 of main rotor 28 and including an outwardly extending set of rotor blades 4l, which are inclined with respect to the axis of the rotor but in a sense opposi-te to the inclination of the blades 3L* of head 2Q. For convenience of assembly the face of rotor l5 adjacent head 29 may be recessed as indicated at 4t. Immediately below said secondary rotor member is a set of stator blades 4S xedly secured to the inside of the wall of said casing i. -Said stator blades i9 extend radially inwards of the casing l and support a substantially streamline portion 43 which is hollow and open at the larger end thereof adjacent said secondary rotor member to allow the hub 5t of said rotor 45 and the end of shaft dil to project thereinto. Said streamline portion acts to direct the incoming liquid towards the stator blades 49 in a funnellike stream. It will be observed that in the vicinity of the afore-mentioned sets of rotor blades the casing i is slightly recessed so as to provide a clearance for the blades 4l, of the secondary rotor 45, and the blades Sil, of the main rotor 28, since these blades not only have to be of the full radial width of the stator blades I3 but are also enclosed by a circumferential guard ring 5l, 52, for the rotor 23 and the secondary rotor 45, respectively.

The end of the shaft 4d remote from the secondary rotor member :i5 extends well beyond the shank 2l to receive an inverted conical gear 53 between the inner end of which and the opposed end of the shank 2l', a thrust-bearing, such as the ball bearing Eli is provided.

Said inverted conical gear 53 is fast on the shaft 4t and said shaft extends beyond said inverted conical gear 53 to provide an end 55 adapted to be coupled to a motor shaft which may extend axially of the pump from a suitable source of power (not shown). On the free end of the head member S I provide a bearing support 55 adapted t0 receive an auxiliary shaft 5i extending radially with respect to the shaft 45 and having an inner end on which a conical gear 58 is xed, which gear meshes simultaneously with gears 55 and 53 so as to drive the gear 35 oppositely with respect to the gear 53 and hence with Y has already been explained the conical gear 53 is fast on the shank 21 of the main rotor 28.

whereas the secondary rotor 45 is fast on the shaft 4G it will be understood that when the shaft 40 is caused to rotate in one direction the main rotor 28 will rotate in the opposite direction and therefore also in the opposite direction with respect to the secondary rotor 45.

The end of shaft 5'! remote from gear 58 may terminate at the outer face of the bearing support 56 or the shaft 5l may be extended outwardly to be coupled to a driving means not shown which would then replace the driving means connected to the end 55 of shaft 40. The purpose of this alternative arrangement for driving the pump will be explained hereinbelow.

To protect the gears 35, 53, and 58 and also to provide a grease chamber for lubricating said gears and the other-rotating said parts of the pump, I provide a cap member 59 suitably secured as by screws 5i) passing through flange V5I of said cap member. At a suitable point in the cap member I provide a filler hole 52 normally closed as by a screw plug 63. The cap member may also be conveniently provided with a gland or stuffing box 64 for the end 55 of the shaft 4i) whilst between the flange 6| of the cap member 59 and the seat 55 there may be inserted a packing 65.

For the purposes of describing the operation of the pump according to this invention it will be assumed that the shaft 45 is connected as shown in Figure l to a coaxial driving shaft 53, since any minor changes in the wording of the description which Va lateral drive might necessitate will readily be understandable by those skilled in the art.

If the pump is installed as is shown in Figure 1 and power is transmitted thereto through the shaft 53, the shaft 49 which is directly coupled to the driving shaft 53 and which has fast on it the secondary rotor 45, will be positively and. directly rotated to drive said secondary rotor 45 in a given sense, say clockwise when viewed as shown in Fig. 3.

The blades @l of the secondary rotor 45 are, as already stated, inclined with respect to the axis of the secondary rotor and they are so inclined that their lower edges 65, that is tc say the edges adjacent the stator blades 49, are the leading edges. Ience rotation of said auxiliary rotor 45 will create a suction lengthwise of the pump and towards the output end thereof whereby liquid is drawn in through the inlet 3 (if desired after passing through a filter or other auxiliary device not shown) into the casing l, where the streamline portion 43, as previously indicated, spreads and directs the liquid into a funnel shaped mass which is subdivided intoa plurality'of streams flowing past stator blades 4l. `Said streams are caught up bythe blades 47 of secondary rotor 45 and owing to the shape of said blades the water is given an additional axial impulse as well as being subjected to the centrifugal forces produced by said rotor 4l as is usual in turbine constructions. The streams of water thrown up by the individual rotor blades 47, are cast against the blades 30 of the main rotor 29 which is rotating in a contrary direction, that is to say, anti-clockwise in Figure 3.

The eect of the impact of the Istreams of water against the rotor blades 3) and of the change in direction of rotation is to acld a still further impulse in a generally axial direction to the streams, which on issuing from the ends of the blades 3B, remote from the secondary rotor are caused to impinge against the upper stator blades i3 which are xed but are shaped and inclined in general similarly to the shape and inclination of the blades 4l of the secondary rotor 155, but in addition are inclined inwardly and upwardly following the longitudinally arcuate shape of the chamber l2. Said upper stator blades I3 direct the streams of water first into the annular space 2d and thence into the passage H of the discharge extension 9.

It will therefore be understood that in passing through the pump the water is first spread out as it were and guided towards the sides of the pump and is then subjected to two active stages of turbine effect whereby a high degree of lift as well as a high Velocity flow in the axial direction and consequently a very considerable capacity are obtained by means of a relatively simple combination of mechanical parts.

It might be though that the omission of a stator between the two rotors in order to change the direction of flow in the manner usual in turbines, and the further fact that the two rotors rotate in opposite directions, would not give the result claimed. However contrary to such expectations experiment has shown that the advantageous results indicated herein above are in fact that the novel pump of the present invention does have a greater lifting power than known centrifugal pumps of similar dimensions and a greater capacity than conventional gear pumps of similar dimensions. In the course of the investigations leading to the present invention experiments were made with turbine type structures comprising a series of pairs of alternating rotors and stators and when the present structure was tested against such other structure it was found that the present structure -gives results comparable to a rotor stator series structure having twice as many pairs of elements as there are rotors in the pump of the present invention. The reason for this remarkable diiierence in results is not entirely clear but it is supposed that the combination of the shape of the rotor blades and the contrary rotations thereof is responsible for the increased overall eectiveness of the pump.

I claim:

1. A rotary turbine pump comprising a casing having an inlet at one end and a hollow outlet extension at the opposite end, a streamline portion centrally located inside said casing adjacent said inlet end, a plurality of first stator blades extending radially between said casing and said streamline portion, a centrally disposed shaft extending lengthwise into said casing from said other end, bearing means secured to said casing and rotarily supporting said shaft, a secondary rotor fast on said shaft adjacent said streamline portion, said secondary rotor including radial and helical blades inclined in a first direction with respect to the axis of said shaft, said secondary rotor blades being substantially coextensive radially with said first stator blades, a first guard ring coaxial with said shaft surrounding said secondary rotor blades and secured thereto, a shank mounted for rotation on said shaft and including an inner end and an outer end extending beyond said other end of the casing, a main rotor fast on said shank adjacent said inner end and adjacent said secondary rotor, a plurality of main rotor blades radially and helically disposed about said main rotor and inclined in a second direction opposed to said first direction with respect tol the axis of said shaft, an annular chamber provided in said casing and having an open end adjacent said main rotor on the side thereof remote from `said secondary rotor and an upper end communicating with said hollow outlet extension, a plurality of second stator blades radially and helically disposed in said chamber with respect to the axis of said shaft and inclined in said iirst direction and positive driving means operatively associated with said shaft and said shank for driving said shaft in one direction and said shank in the opposite direction.

2. A rotary turbine pump comprising a cylindrical casing having a constricted inlet at one end, a head member including a spigot at one end and a hollow outlet extension excentrically disposed at the other end, said spigot having a free end and extending into and being secured to the end of the casing remote from the inlet, said head member including the spigot being centrally and axially bored, an annular chamber formed in said spigot and extending axially thereof from said free end between said bore and said casing, a streamline portion centrally located adjacent said inlet and extending thereinto, said streamline portion being spaced from said casing, a plurality of first stator blades extending radially between said casing and said streamline portion and supporting said streamline portion, a plurality of second stator blades in said chamber disposed radially and helically therewithin, said second stator blades being inclined in a first direction with respect to the axis of the casing, a main rotor member including a shank and a plurality of main rotor blades arranged helically and radially about said rotor member, said shank being housed for rotation in said bore and said main rotor blades being radially coextensive with said second ystator blades, and being inclined in a second direction opposed to said first direction, said main rotor blades being disposed in said casing with one end adjacent said second stator blades and being surrounded by a guard ring secured thereto, said shank being hollow to provide an inner bore, a shaft located for free rotation in said inner bore and having an outer end extending beyond said end member and an inner end, a secondary rotor mounted on said inner end and including a plurality of secondary rotor blades disposed axially and helically about said secondary rotor and inclined in said first direction, said secondary rotor being located between said first stator blades and said first rotor, a bearing support mounted on the end of the head member remote from the spigot, a stub shaft supported for rotation on said bearing support, a first bevel gear fast on said shank, a second bevel gear fast on said shaft on the side of said first bevel gear remote from said head member and a third bevel gear fast on said stub shaft and simultaneously meshing with said first and second bevel gear to cause said shaft and said shank to be rotated in opposite directions when power is applied to the pump.

GUILLERMO FEDERICO BAEZ.

REFERENCES CITED The following references are of record in the 

